Fluid translator

ABSTRACT

The specification discloses a fluid operated rotary motor which includes a circular rotor rotatably mounted between two opposed walls. The rotor has grooves spaced about the periphery thereof to define a plurality of pistons. Pressure inlet and exhaust outlet ports are formed through the side walls of the rotor in order to communicate with the grooves. The ports periodically communicate with the slots in the walls during rotation of the rotor to effect valving. A plurality of circular heads are rotatably mounted between the opposed walls and are spaced about the periphery of the rotor such that portions of the cylinder heads are received within the grooves. Plural cylinder grooves are defined in the edges of each of the cylinder heads in order to receive the pistons. Gears are provided to synchronize the rotation of the cylinder heads with the rotor. Pressurized fluid is applied through the slots in one of the walls and through the pressure inlet ports into the grooves in order to rotate the rotor and the cylinder heads. The pressurized fluid is then exhausted from the grooves through the exhaust outlet ports and through the slots formed in the other of the side walls. A second motor unit may be oriented at an angle to the first motor unit in order to provide uniform rotation to an output shaft keyed to the rotors of both of the motor units.

United. States Patent 11 1 Miller 1 1 .Dec. 3, 1974 1 1 FLUID TRANSLATOR R. J. Pollard. San Marcos, Tex.; a part interest [22] Filed: Apr. 26, 1973 [21] Appl. No.: 354,802

[73 ]v Assignee:

[52] US. Cl. 418/196, 418/186 [51] Int. Cl. F01C 1/08 [58] Field of Search 418/196, 186

[56] 1 References Cited UNITED STATES. PATENTS 507.738 10/1893 Kcttron 418/196 622949 4/1899 Green 418/186 926,641 6/1909 (otl'ey et all. 418/196 995,505 6/1911 Weddinglon.... 418/186 1.052.045 2/1913 Doedyns 418/196 1.238.467 8/1917 Wherry.... 418/196 1,766,519 6/1930 Johnson... 418/196 2.088.121 7/1937 Swink 418/196 2.180.377 11/1939 Whitfield 418/196 2,274,569 2/1942 Weinberger 418/196 2,681,621 6/1954 Hedman. 418/196 3,116,666 1/1964 Scott 418/196 3.416.458 12/1968 Kopfli 418/196 Primary ExaminerC. J. l-lusar Attorney, Agent, or FirmRichards, Harris & Medlock l 5 7 l ABSTRACT The specification discloses a fluid operated rotary motor which includes a circular rotor rotatably mounted between two opposed walls. The rotor has grooves spaced about the periphery thereof to define a plurality of pistons. Pressure inlet and exhaust outlet ports are formed through the side walls of the rotor in order to communicate with the grooves. The ports periodically communicate with the slots in the walls during rotation of the rotor to effect valving. A plurality of circular heads are rotatably mounted between the opposed'walls and are spaced aboutthe periphery of the rotor such that portions of the'cylinder heads are received within the grooves. Plural cylinder grooves are defined in the edges of each of the cylinder heads in order to receive the pistons. Gears are provided to synchronize the rotation of the cylinder heads with the rotor. Pressurized fluid is applied through the slots in one of the walls and through the pressure inlet ports into the grooves in order to rotate the rotor and the cylinder heads. The pressurized lluid is then exhausted from the grooves throughthe exhaust outlet ports and through the slots formed in the other of the side walls. A second motor unit may be oriented at an angle to the first motor unit in order to provide uniform rotation to an output shaft keyed to the rotors of both of the motor units.

13 Claims, 8 Drawing Figures FLUID TRANSLATOR FIELD OF THE INVENTION This invention relates to motors, and more particularly relates to a rotary motor operated by pressurized fluid. i

THE PRIOR ART A variety of different types of rotary engines have been herebefore developed wherein pressurized fluid such as steam or the like has been converted into mechanical rotary motion. A number of previous rotary motors of this type utilize a central rotor and a plurality of cylinder heads which are disposed about the periphery of the rotor in order to effect valving of the pressurized fluid through the rotor. Examples of such previously developed rotary motors may be found in U.S. Pat. No. 1,969,620 issued to Mau; U.S. Pat. No. 2,152,564 issued to Perkins; and U.S. Pat. No. 3,1 16,666 issued to Scott.

However, such previously developed rotary engines have not been completely satisfactory with respect to voutput power and vibration characteristics. Problems have also herebefore been experienced with respect to lubrication and with respect to satisfactory internal sealing of the rotating parts of such prior motors.

SUMMARY OF THE INVENTION In accordance with the present invention, a rotary engine is provided of a design which enables the use of extremely close tolerances and therefore eliminates many problems herebefore encountered relative to sealing between rotating parts. The present engine provides essentially uniform torque for substantial magnitude without the occurrence of significant vibration.

In accordance with a more specificaspect of the invention, a casing includes opposed wall plates with slots symetrically formed through the walls. A circular rotor is rotatably mounted between the opposed walls and has grooves spaced about the periphery thereof to define a plurality of piston surfaces. Pressure inlet and exhaust outlet ports are formed through the side walls of the rotor to communicate with the grooves. The ports thus periodically communicate with the slots in the wall plates during rotation of the rotor. A plurality of circular cylinder heads are rotatably mounted between the opposed wall plates and are spaced about the periphery of the rotor such that portions of the cylinder heads are received within the grooves. Plural cylinder grooves are defined in the edges of each of the cylinder heads for receiving the piston surfaces. Gears synchronize the rotation of the cylinder heads with the rotor. Pressurized fluid is thus applied through the slots in one of the wall plates and through the pressure inlet ports and through the grooves in order to rotate the motor. The pressurized fluid is then exhausted from the grooves through the exhaust outlet ports and through the slots formed in the wall plates.

In accordance with a more specific aspect of the invention, a casing includes a first side plate having four arcuate pressure inlet slots spaced apart in a circular configuration. The casing further includes a second side plate including four arcuate exhaust outlet slots spaced apart in acircular configuration. A circular rotor has an output shaft rotatably mounted between the side plates. The rotor has four groove portions formed about the periphery thereof to define four pistons having surfaces coextensive with the periphery of the rotor. Four pressure inlet ports are formed through a first side wall of the rotor to communicate with each of the groove portions. Four exhaust outlet ports are formed through a second side wall of the rotor to communicate with each of the groove portions. The pressure inlet ports periodically communicate with the inlet slots and the exhaust outlet ports periodically communicate with the outlet slots during rotation of the rotor. Four circular cylinder heads each have cylindrical shafts rotatably mounted between the plates. The cylindrical heads are spaced about the periphery of the rotor such that edge portions of the cylinder heads are reinder heads. The pressurized fluid is then exhaustedfrom the groove portions through the exhaust outlet ports and through the outlet slots in the second side plate.

DESCRIPTION OF THE DRAWINGS For a more complete understanding of the present invention and for further objects and advantages thereof, reference is now made to the following description taken in conjunction with the accompanying drawings, in which:

FIG. 1 is a side view of a motor unit constructed in accordance with the present invention;

FIG. 2 is a sectional view of the motor unit shown in I FIG. 1 taken generally along the section lines 22';

FIG. 3 is a perspective view of the rotor and one of the cylinder heads of the invention shown in an exploded relationship to the pressure inlet side plate;

FIG. 4 is a sectional view taken generally along the section lines 44 in FIG. 2;

FIG. 5 is a sectionalview of a pair of motor units oriented at an angle relative to one another in accordance with the invention;

FIG. 6 is a somewhat diagramatic side illustration of the gearing system shown in FIG. 5;

FIG. 7 is a sectional view taken through the rotor and one of the cylinder heads of the invention immediately adjacent one of the pistons in the rotor during the admission of pressurized fluid thereto; and

FIG. 8 is a sectional view of the rotor and cylinder head of FIG. 7 during the exhaust cycle.

DESCRIPTION OF THE PREFERRED EMBODIMENT FIG. I is a side view of a motor unit 10 constructed a in accordance with the present invention. As will be subsequently described, in the preferred embodiment at least two motor units will generally be coupled together in an angled configuration in order to provide smooth operation.

Referring to FIG. 1, the motor unit 10 includes a side plate 12 having mounted on the interior side thereof a rotor 14 and four circular cylinder heads l6a-d. The cylinder heads 16a-d each include a pair of cylinder grooves l8a-d and 20a-d. Each of the cylinder grooves comprises a circular groove extending across the width of the cylinder head and having an opening which extends across the width of the cylinder head at the periphery thereof. Each of the cylinder grooves l8a-d are disposed on the opposite sides of the cylinder heads from the cylinder grooves 20a-d. The rotor 14 is rotatably mounted relative to the plate 12 by a shaft 22. The cylinder heads 16a-d are rotatably mounted relative to the plate 12 on shafts 24a-d.

As will be subsequently described, the shafts 22 and 24a-d are connected through suitable gearing so that the rotor 14 rotates in synchronism with rotation of the cylinder heads 16a-d.

Four arcuate pressure inlet slots 26a-d are defined through the plate 12 and remain stationary during operation of the motor unit 10. As shown in FIG. 2, a second plate 28 is disposed on the opposite side of the motor unit from plate 12. FIG. 1 illustrates four arcuate exhaust slots 30a-d which are defined through the plate 28. It will thus be understood that slots 26a-d are stationarily disposed on one side of the rotating rotor 14, while slots 30a-d are stationarily disposed on the other side of the rotor 14.

Pressure inlet ports 32a-d are defined through the side of the rotatable rotor 14. Similarly, exhaust outlet ports 34a-d are defined through the opposite side of the rotatable rotor 14. As will be subsequently shown in greater detail, four grooves 38a-d are symetrically defined about the periphery of the rotatable rotor 14. Portions of the cylinder heads 16a-d fit within the grooves 38a-d, with a close tolerance fit provided between the peripheries of the cylinder heads and the bottom of the grooves 38a-d. The grooves 38a-d form pistons 40a-d at the outer periphery of the rotor 14. As shown in FIG. 1, pistons 40a-d have a curved outer edge and inwardly curved interior sides. The pistons 40u-d are closely received within the cylinder grooves a-d of the cylinder heads. In the preferred embodiment, the rotor 14 and the cylinder heads I6a-d are constructed from metal and a close tolerance metal-tometal seal is provided between the pistons 40a-d and the cylinder grooves 18a-d and 20a-d.

FIG. 2 is a sectional view taken generally along the section lines 2-2 of the motor unit 10 shown in FIG. 1. Plates l2 and 28 are integral portions of a housing including outer walls 42 and 44. The power shaft 22 is keyed to the rotor 14 and extends through the plates 12 and 28 and through the housing walls 42 and 44. One end of the shaft 22 is directed to a gear system for interconnection with the shafts 24a-d, while the other end of the shaft 22 extends as a power output shaft. Chambers 46 and 48 communicate with one another and with a pressure inlet port 50 to receive a suitable source of pressurized fluid. The fluid may comprise for example, steam, compressed air or other gas or liquids under pressure. The pressurized fluid passes from the chamber 46 through the slots 26a-d and through the ports 32a-d into the grooves 38a-d formed in the periphery of the rotor 14. The pressurized fluid causes rotation of the rotor 14 relative to the cylinder heads 16a-d. The pressurized fluid is then exhausted through the ports 34a-d and through the slots 30a-d to an exhaust chamber 52. The pressurized fluid is then exhausted through an exhaust outlet 54. Rotation of the rotor 14 causes rotation of the power output shaft 22 in order to drive any suitable machine.

FIG. 3 illustrates a perspective view of the rotor 14 and of one of the cylinder heads 16c, along with plate 28 exploded away from the rotor and cylinder head in order to illustrate the exhaust slots 30c-d. The remaining cylinder heads 16a-b and 160 are omitted for clarity of illustration. FIG. 3 clearly illustrates the grooves 38c-d and shows how the main body of the cylinder head 160 is received within the grooves. As the rotor 14 and cylinder head 16 rotate relative to one another about their respective shafts 22 and 24c, the cylinder grooves 180 and 200 mesh with the pistons a-d. The ports 32a-d are illustrated as extending through the outer peripheral edges of the rotor 14 and into communication with the slots 30a-d. The exhaust ports 34a-a' extend through the opposite side of the rotor 14 in communication with the grooves 38a-d. The cylinder head 16c includes annular extensions 60 on both sides thereof. The extensions 60 are dimensioned to .004 inch clearance of the outer periphery of the rotor 14 in the manner illustrated.

FIG. 4 is a sectional view taken generally along section lines 4--4 of FIG. 2, and illustrates the exhaust side of the motor unit 10. FIG. 4 also illustrates with clarity the construction of the grooves 38a-d and the pistons 40a-d. The pressure inlet ports 32a-d are also illustrated. FIG. 4 illustrates the closeness of the fit between the outer peripheries'of the cylinder heads l6a-d and the bottom of the grooves 38a-d, and it will thus be understood how the admittance of pressurized fluid into the grooves 38a-d exerts sufficient force between the pistons 40a-d and the rotor 14 and the cylinder heads 16a-d to cause rotation of the rotor 14.

FIG. 5 illustrates a sectional view of the preferred embodiment of the invention, wherein two motor units 70 and 72 constructed in accordance with the invention are mounted in a bank-to-back configuration in order to provide smooth operation. The motor unit includes an output shaft 74 which is keyed to a rotor 76. Cylinder heads 78 are disposed of about thequadrants of the rotor 76 in the manner previously described. The cylinder heads are rotated about shafts 80 which are connected to a gearing system 82. Gearing system 82 interconnects the cylinder heads 78 with the rotor 76 so that the rotation thereof is synchronized.

Motor unit 72 also includes a rotor 84 which is keyed to the output shaft 74 and includes four cylinder heads 86 disposed about the quadrants of rotor 84 in the manner previously described. An important aspect of the invention is that the motor unit 72 is oriented at a 45 angle relative to motor unit 70 to provide generally constant output torque to the shaft 74. Pressurized fluid is supplied via conduit 88 and is applied to a pressure chamber 90 and a pressure chamber 92. Fluid from chamber 90 passes through slots 94 to the rotor 76 in the manner previously described and is exhausted via slots 96 to an exhaust conduit 98. Pressurized fluid is also applied to a chamber 100 and passes through ports 102 to the rotor 84. Exhausted pressurized fluid is passed through exhaust slots 104 and out an exhaust conduit 106.

FIG. 6 is a side view of the gearing system 82 and includes a central gear 108 and eight peripheral gears 110. The gearing unit 82 thus transmits rotative motion from the rotor 76 through the gear 108 and gears 110 to the cylinder heads associated therewith, so that the cylinder heads rotate in synchronism with rotation of the rotor.

FIG. 7 illustrates application of pressurized fluid in front of the piston 40 of the rotor in order to apply rotative force to the rotor. The plate 12 includes the slot 26 therein as previously described. The pressure inlet port 32 is defined through one side of the outer periphery of the rotor 14. The rotating cylinder head 16 fits between the grooves of the rotor and between plates 12 and 28 with a close tolerance, such as, for example, a tolerance of .004 inch. The piston 40 of the rotor 14 is illustrated as including an upper curved surface 112 to provide a sufficient surface for sealing between the rotating cylinder head. In operation of the system, pressurized fluid is applied through the slot 26 and the port 32 and applies pressure between the curved side of the piston 40 and the rotating cylinder heads 16 in order to rotate the rotor 14.

FIG. 8 illustrates'a similar view as that shown in FIG. 7 during the exhaust cycle of operation of the system. The slot 30 is defined through plate 28 and communicates with the exhaust port 34 of the rotor'14. The rearward side of the piston 40 thus serves to operate against the relatively moving cylinder groove to exhaust pressurized fluid from the groove 38 through the port 34 and slot 30.

While motor units including four cylinder heads have been disclosed, it will'be understood that the present invention contemplates the use of other arrangements, such as a rotor with only two cylinder heads and piston arrangements, or other combinations of cylinder heads and pistons. The speeds of rotation and relative sizes of the rotors and cylinder heads of course vary for various applications, but a rotational speed between the rotor and cylinder heads of 2:] has been found to work well. Lubrication would be required for shaft bearings, which have been omitted in the drawings for clarity of illustration, and for the gears. It is believed that no other lubrication is required within the motor units of the invention, due to the close tolerances allowed by the present design.

The present invention thus provides an excellent motor for use withexternal combustion power systems for example, wherein a converter for pressure and/or heat energy into torque force for rotational machinery is desired. The particular configuration of the device enables the pistons to pass through associated cylinders in a relatively short space of rotation and with maximum pressure sealing area at the top of the piston. In addition, the device will result in relatively little back pressure on the cylinder head and therefore little resistance to rotation, thus allowing essentially the total force or pressure behind the piston to be applied to the piston as torque on the rotor. The unique technique for valving the particular arrangement of this particular invention does not require individual moving parts as it requires only slots and ports which can be machined into the individual parts with extreme precision. The utilization of two of the motor units of the invention at an angularly orientated configuration enables essentially constant torque to be applied to the output shaft without torque pulses. Due to the generally symetrical configuration of the devices, little vibration is provided by the system when balanced.

Whereas the present invention has been described with repsect to specific embodiments thereof, it will be understoodthat various changes and modifications will be suggested to one skilled in the art, and it is intended to encompass such changes and modifications as fall within the scope of the appended claims.

What is claimed is:

-1. A rotary motor comprising:

a casing having opposed walls with elongate slots symmetrically formed through said walls,

a circular rotor rotatably mounted between said opposed walls and having grooved portions extending into the periphery of said rotor and spaced about the periphery thereof to define a plurality of piston surfaces, the outer surfaces of said piston surfaces being adjacent the periphery of said rotor,

pressure inlet and exhaust outlet ports formed through opposed sidewalls of said rotor to communicate with said grooved portions, said ports periodically communicating with said slots in said walls during rotation of said rotor,

a plurality of circular cylinder heads rotatably mounted between said opposed walls and spaced about the periphery of said rotor such that outer portions of said cylinder heads mate with and are closely received within said grooved portions,

plural cylindergrooves being defined in the edges of each said cylinder head, said cylinder grooves being dimensioned for receiving said piston 'surfaces,

means for synchronizing the rotation of said cylinder heads with said rotor, and

means for applying pressurized fluid through said slots in one of said walls and through said pressure inlet ports into said grooved portions in order to rotate said rotor and said cylinder heads, said pressurized fluid being exhausted from said grooved portions through said exhaust outlet ports and through said slots formed in one of said walls.

2. The motor of claim 1 wherein four cylinder heads are disposed symetrically about said rotor.

3. The motor of claim 1 wherein each of said cylinder heads includes a pair of cylinder grooves spaced from one another on said cylinder heads.

4. The motor of claim 1 wherein said synchronizing means comprises a gear system.

5. The motor of claim 1 wherein said slots have arcuate configurations to correspond with the path of travel of said ports.

6. The motor of claim 1 and further comprising:

a second rotary motor oriented at an angle and disposed adjacent to said rotary motor, and

shaft means for being driven by both said rotary motors.

7. A rotary motor assembly comprising:

first and second rotary motors commonly connected to an output shaft and oriented at an angle to one another, each of said motors comprising:

a casing having a first side plate having four arcuate pressure inlet slots spaced apart in a circular configuration, 4

said casing further having a second side plate including four arcuate exhaust outlet slots spaced apart in a circular configuration,

a circular rotor connected to said output shaft rotatably mounted between said side plates,

said rotor having four grooved portions formed about the periphery thereof to define four pistons having surfaces coextensive with the periphery of said rotor,

four pressure inlet ports formed through a first sidewall of said rotor to communicate with each of said grooved portions,

four exhaust outlet ports formed through a second opposed sidewall of said rotor to communicate with each of said grooved portions,

said pressure inlet ports periodically communicating with said inlet slots and said exhaust outlet ports periodically communicating with said outlet slots during rotation of said rotor,

four circular cylinder heads each having cylinder shafts rotatably mounted between said plates, said cylinder heads spaced about the periphery of said rotor such that edge portions of said cylinder heads are closely received within said grooved portions,

each of said cylinder heads having a pair of cylinder grooves formed in opposite sides thereof, said cylinder grooves being dimensioned to receive said pistons,

gears interconnecting said output shaft and said cylinder shafts for synchronizing the rotation of said cylinder heads with said rotor, and

means for applying pressurized fluid through said pressure inlet slots and said pressure inlet ports into said grooved portions in order to rotate said rotor and said cylinder heads, said pressurized fluid being exhausted from said grooved portions through said exhaust outlet ports and through said outlet slots in said second side plate.

8. The rotary motor of claim 7 wherein said pressure inlet ports communicate with first ends of said grooved portions and said exhaust outlet ports communicate with second ends of said grooved portions.

9. The motor of claim 7 wherein said pistons comprise an upper curved surface and opposed inwardly curved side walls.

10. The motor of claim 7 wherein each of said cylinder heads includes circular extensions on opposite sides thereof, the outer edges of said circular extensions generally abutting the outer peripheral edges of said rotor.

11. The motor of claim 7 wherein said ports in said rotor are symmetrically disposed between said pistons.

12. The motor of claim 7 wherein said motors are oriented at 45 to one another.

13. The motor of claim 7 wherein said gears comprise:

a central large gear connected to said output shaft and a plurality of small gears disposed about the periphery of said large gear and connected to said cylinder shafts. 

1. A rotary motor comprising: a casing having opposed walls with elongate slots symmetrically formed through said walls, a circular rotor rotatably mounted between said opposed walls and having grooved portions extending into the periphery of said rotor and spaced about the periphery thereof to define a plurality of piston surfaces, the outer surfaces of said piston surfaces being adjacent the periphery of said rotor, pressure inlet and exhaust outlet ports formed through opposed sidewalls of said rotor to communicate with said grooved portions, said ports periodically communicating with said slots in said walls during rotation of said rotor, a plurality of circular cylinder heads rotatably mounted between said opposed walls and spaced about the periphery of said rotor such that outer portions of said cylinder heads mate with and are closely received within said grooved portions, plural cylinder grooves being defined in the edges of each said cylinder head, said cylinder grooves being dimensioned for receiving said piston surfaces, means for synchronizing the rotation of said cylinder heads with said rotor, and means for applying pressurized fluid through said slots in one of said walls and through said pressure inlet ports into said grooved portions in order to rotate said rotor and said cylinder heads, said pressurized fluid being exhausted from said grooved portions through said exhaust outlet ports and through said slots formed in one of said walls.
 2. The motor of claim 1 wherein four cylinder heads are disposed symetrically about said rotor.
 3. The motor of claim 1 wherein each of said cylinder heads includes a pair of cylinder grooves spaced 180* from one another on said cylinder heads.
 4. The motor of claim 1 wherein said synchronizing means comprises a gear system.
 5. The motor of claim 1 wherein said slots have arcuate configurations to correspond with the path of travel of said ports.
 6. The motor of claim 1 and further comprising: a second rotary motor oriented at an angle and disposed adjacent to said rotary motor, and shaft means for being driven by both said rotary motors.
 7. A rotary motor assembly comprising: first and second rotary motors commonly connected to an output shaft and oriented at an angle to one another, each of said motors comprising: a casing having a first side plate having four arcuate pressure inlet slots spaced apart in a circular configuration, said casing further having a second side plate including four arcuate exhaust outlet slots spaced apart in a circular configuration, a circular rotor connected to said output shaft rotatably mounted between said side plates, said rotor having four grooved portions formed about the periphery thereof to define four pistons having surfaces coextensive with the periphery of said rotor, four pressure inlet ports formed through a first sidewall of said rotor to communicate with each of said grooved portions, four exhaust outlet ports formed through a second opposed sidewall of said rotor to communicate with each of said grooved portions, said pressure inlet ports periodically communicating with said inlet slots and said exhaust outlet ports periodically communicating with said outlet slots during rotation of said rotor, four circular cylinder heads each having cylinder shafts rotatably mounted between said plates, said cylinder heads spaced about the periphery of said rotor such that edge portions of said cylinder heads are closely received within said grooved portions, each of said cylinder heads having a pair of cylinder grooves formed in opposite sides thereof, said cylinder grooves being dimensioned to receive said pistons, gears interconnecting said output shaft and said cylinder shafts for synchronizing the rotation of said cylinder heads with said rotor, and means for applying pressurized fluid through said pressure inlet slots and said pressure inlet ports into said grooved portions in order to rotate said rotor and said cylinder heads, said pressurized fluid being exhausted from said grooved portions through said exhaust outlet ports and through said outlet slots iN said second side plate.
 8. The rotary motor of claim 7 wherein said pressure inlet ports communicate with first ends of said grooved portions and said exhaust outlet ports communicate with second ends of said grooved portions.
 9. The motor of claim 7 wherein said pistons comprise an upper curved surface and opposed inwardly curved side walls.
 10. The motor of claim 7 wherein each of said cylinder heads includes circular extensions on opposite sides thereof, the outer edges of said circular extensions generally abutting the outer peripheral edges of said rotor.
 11. The motor of claim 7 wherein said ports in said rotor are symmetrically disposed between said pistons.
 12. The motor of claim 7 wherein said motors are oriented at 45* to one another.
 13. The motor of claim 7 wherein said gears comprise: a central large gear connected to said output shaft and a plurality of small gears disposed about the periphery of said large gear and connected to said cylinder shafts. 